CA2060980A1 - Scroll type compressor - Google Patents
Scroll type compressorInfo
- Publication number
- CA2060980A1 CA2060980A1 CA 2060980 CA2060980A CA2060980A1 CA 2060980 A1 CA2060980 A1 CA 2060980A1 CA 2060980 CA2060980 CA 2060980 CA 2060980 A CA2060980 A CA 2060980A CA 2060980 A1 CA2060980 A1 CA 2060980A1
- Authority
- CA
- Canada
- Prior art keywords
- movable
- stationary
- tip
- spiral body
- discharging port
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000007599 discharging Methods 0.000 claims abstract description 39
- 239000012530 fluid Substances 0.000 claims abstract description 5
- 238000007906 compression Methods 0.000 claims description 22
- 230000006835 compression Effects 0.000 claims description 21
- 238000007789 sealing Methods 0.000 claims description 6
- 229920001343 polytetrafluoroethylene Polymers 0.000 claims description 5
- 239000004810 polytetrafluoroethylene Substances 0.000 claims description 5
- 230000003247 decreasing effect Effects 0.000 claims description 3
- -1 polytetrafluoroethylene Polymers 0.000 claims description 3
- 238000009987 spinning Methods 0.000 claims description 2
- 239000011347 resin Substances 0.000 claims 1
- 229920005989 resin Polymers 0.000 claims 1
- 239000002826 coolant Substances 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 4
- 230000006872 improvement Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- KUVIULQEHSCUHY-XYWKZLDCSA-N Beclometasone Chemical compound C1CC2=CC(=O)C=C[C@]2(C)[C@]2(Cl)[C@@H]1[C@@H]1C[C@H](C)[C@@](C(=O)COC(=O)CC)(OC(=O)CC)[C@@]1(C)C[C@@H]2O KUVIULQEHSCUHY-XYWKZLDCSA-N 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 101150008563 spir gene Proteins 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0253—Details concerning the base
- F04C18/0261—Details of the ports, e.g. location, number, geometry
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
SCROLL TYPE COMPRESSOR
ABSTRACT OF THE DISCLOSURE
In a scroll type compressor, a discharging port in a side plate of a stationary scroll member is formed in an elongated shape, such as an oval, so that a tip-seal element provided in the beginning area of a movable spiral body does not interfere with the discharging port in the course of an orbital motion, whereby damage to the tip-seal element due to a draw-in thereof to the discharging port can be avoided, while ensuring a sufficient fluid pressure and full sealability.
(Fig. 2)
ABSTRACT OF THE DISCLOSURE
In a scroll type compressor, a discharging port in a side plate of a stationary scroll member is formed in an elongated shape, such as an oval, so that a tip-seal element provided in the beginning area of a movable spiral body does not interfere with the discharging port in the course of an orbital motion, whereby damage to the tip-seal element due to a draw-in thereof to the discharging port can be avoided, while ensuring a sufficient fluid pressure and full sealability.
(Fig. 2)
Description
- 1 - 2~6~980 SCROLL TYPE COMPRESSOR
BACKGROUND OF ~HE INVENTION
1. Field of the Invention The present invention relates to a scroll type compressor, particularly to an improvement of the sealability for a beginning area of a spiral body in a movable scroll member and an improvement of a discharging port of a stationary scroll member in the compressor.
BACKGROUND OF ~HE INVENTION
1. Field of the Invention The present invention relates to a scroll type compressor, particularly to an improvement of the sealability for a beginning area of a spiral body in a movable scroll member and an improvement of a discharging port of a stationary scroll member in the compressor.
2. Description of the Related Arts As shown in Fig. 6, the conventional scroll type compressor comprises a stationary scroll member 52 fixed in a housing 51, and a movable scroll member 53 rotatably accommodated in the housing 51. The stationary scroll 52 member consists of a stationary side plate 21 and a stationary spiral body 22 comprising outer and inner walls defined, respectively, by an involute curve or other and integrally fixed on one surface of the stationary side plate 21. ~The movable scroll member 53 consists of a movable side plate 31 and a movable spiral body 32 comprising outer and inner walls defined, respecti~ely, by an involute curve or other and integrally fixed on one surface of the side plate 31, both spiral bodies 22 and 32 being engaged with each other with a phase difference of 180~ therebetween.
Grooves 22a and 32a are formed, respectively, along ridges of the stationary and movable spiral bodies 22 and 32, extending in the spiral direction thereof. As shown in Fig. 7, tip seal elements 22b and 32b are accommodated in the grooves 22a, 32a, respectively, for sealing a gap between the spiral bodies 22, 32 and the side plates 31, 21.
As shown in Fig. 6, the rotation of a drive shaft 54 is converted to an orbital motion of the movable scroll member 53 through an eccentric bush 57 and an anti-spin mechanism 58. The structures and functions of - 2 - 2~6 0~0 the eccentric bush and the anti-spin mechanism are described in detail in, for example, Japanese Unexamined Patent Publication (Xokai) No. 57-148087 or 57-148092.
According to the orbital motion of the movable scroll S member 53, a volume of a compression chamber 55 formed between the scroll members 52, 53 is gradually decreased while the compression chamber 55 is displaced to a central area of the scroll members, whereby a fluid in the compression chamber 55 is compressed and finally discharged therefrom through a discharging port 61 of the stationary side plate 21, into a discharging chamber 60.
At this stage, the tip seal element 32b is pressurized from the back by a coolant gas from a high pressure side HP positioned closer to the center of the stationary side plate 21, whereby the tip seal element 32 is brought into tight contact with a wall of the groove 32a adjacent to the low pressure side LP positioned farther from the center of the stationary side plate 21, and brought into tight contact with a surface of the stationary side plate 21 via a film of lubricant contained in the coolant gas, so that the coolant gas is sealed in the compression chamber 55. The tip seal element 22b functions in a similar manner.
In the conventional compressor, the tip seal element 32b is not provided in the beginning area of the movable spiral body 32. This is because, as shown in Fig. 8, the discharging port 61 of the conventional compressor has a circular shape, and if the tip seal element 32b were located in this area, the tip seal element 32b would be liable to be sucked from the groove 32a into the discharging port 61 when the tip seal element 32b overlapped the discharging port 61 in the course of the orbital motion of the movable scroll member 53, whereby the tip seal element 32b would be damaged by the edge of the latter. Accordingly, the conventional compressor has a drawback of an incomplete sealability at the beginning area of the movable spiral ~ 3 ~ 2~609~
body, and as this area is subjected to the maximum pressure during the compression process, a pressure loss is liable to occur.
SUMMARY OF THE INVENTION
The object of the present invention is to solve the above drawback of the prior art and to improve the sealability at the beginning area of the movable spiral body while preventing the damage of the tip seal element.
According to the present invention, a scroll type compressor is proposed, comprising a stationary scroll member consisting of a stationary side plate and a stationary spiral body integrally fixed therewith and a movable scroll member consisting of a movable side plate and a movable spiral body integrally fixed therewith;
both the scroll members being engaged with each other so that a plurality of compression chambers are formed between the scroll members and gradually decreased during an orbital motion of the movable scroll member around the stationary scroll member, while the movable scroll member is inhibited from spinning~on its own axis, whereby a fluid is compressed in the compression chambers and discharged from the compression chamber through a discharging port formed on the stationary side plate; the movable spiral body having a groove along a ridge thereof, extending in the spiral direction, in which groove a tip-seal element is accommodated for sealing a gap between the stationary side plate and the ridge of the movable spiral body; characterized in that the tip-seal element extends to the beginning area of the movable spiral body and in that the discharging port is formed in an elongated shape to thereby avoid an interference thereof with the tip-seal element during the orbital motion of the movable scroll member while a necessary cross-sectional area of the discharging port is maintained.
According to the present invention, the sealability is fully maintained even at the beginning area of the - 4 ~ 2~9~n movable spiral body subjected to the maximum pressure, because the tip-seal element is extended thereto, and thus a pressure loss in the compression chamber is avoided.
Moreover, as the discharging port is formed in an elongated shape, not in a circular shape, so that the interference thereof with the tip-seal element can be avoided and that the necessary cross-sectional area of the discharging port is maintained, a draw-in of the tip seal element from the groove to the discharging port is prevented and damage to the tip-seal element by the edge of the discharging port is avoided, while the necessary discharging efficiency is guaranteed.
BRIEF DESCRIPTION OF THE DRAWINGS
Other and further objects and advantages of the present invention will be apparent from the following description of the preferred embodiments with reference to the attached drawings: wherein Fig. 1 is a side sectional view of a scroll type compressor according to the present invention;
Fig. 2 is A-A section of Fig. l at a certain phase angle of the orbital motion of the movable scroll member;
Fig. 3 is A-A section of Fig. 1 at a phase angle advanced by 90 from that shown in Fig. 2;
Fig. 4 is A-A section of Fig. 1 at a phase angle advanced by 90 from that shown in Fig. 3;
Fig. 5 is A-A section of Fig. l at a phase angle advanced by 90 from that shown in Fig. 4;
Fig. 6 is a side sectional view of a conventional scroll type compressor;
Fig. 7 is an enlarged side sectional view of a main portion of the conventional compressor; and Fig. 8 is a cross-section of a main portion of the conventional compressor.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
As shown in Fig. l, in a scroll type compressor ~ 5 ~ 2~6098~
according to the present invention, a stationary scroll member 2 is fixed within a housing 1, and a movable scroll member 3 arranged in the housing l and a housing 9 is engaged with the stationary scroll member 2 so that a plurality of compression chambers 5 are formed between both the scroll members 2 and 3. A drive shaft 4 is supported in the housings 1, 9 via a bearing means, and an eccentric pin 10 is secured on an inner end surface of the driving shaft 4. At the bearing side end of the eccentric pin 10 is fixed a counterweight 11, and to the other end thereof is attached a driving bush 7 suppoxting the movable scroll member 3 by a bearing means, so that it can be subjected to an orbital motion around the stationary scroll member 2 in association with an anti-spin mechanism 8.
The movable scroll member 3 consists of a movableside plate 14 and an movable spiral body 15 integrally fixed therewith on one side of the side plate 14. As shown in Fig. 2, the movable spiral body 15 is formed by outer and inner walls, eac~h defined, except for the beginning area 151 thereof, by an involute curve obtained from a predetermined basic circle. Only the inner wall of the beginning area 151 is defined by an arc F1 having a radius r, an arc F2 having a radius R (r + radius of orbital motion) and a common tangent F3 for the two arcs.
Along a ridge of the movable spiral body 15 is extended a groove 15a, from the beginning area 151 to the ending area thereof (not shown), while an equal wall thickness is maintained between the groove and the outer wall of the spiral body 15. A tip-seal element 15b made of PTFE
(polytetrafluoroethylene) is accommodated within the groove 15a, for sealing a gap between the stationary side plate 12 and the tip end of the spiral body 15. A more detailed explanation will be made later of the tip-seal element.
As shown in Fig. 1, the stationary scroll member 2 20~0980 consists of a stationary side plate 12 and a stationary spiral body 13 integrally fixed therewith on one side of the side plate 12. As shown in Fig. 2, the stationary spir~l body 13 is formed by outer and inner walls, each defined, except for the beginning area 131 thereof, by an involute curve obtained from a predetermined basic circle. Only the inner wall of the beginning area 131 is defined by an arc Sl having a radius r, an arc S2 having a radius R (r + radius of orbital motion) and a common tangent S3 for the two arcs. Along a ridge of the stationary spiral body 13 is also extended a groove 13a.
A tip-seal element 13b made of PTFE
(polytetrafluoroethylene) is accommodated within the groove 13a, for sealing a gap between the movable side plate 14 and the tip end of the spiral body 13. This tip seal element 13b is provided in the beginning area 131 (although not shown in the drawing), as in the case of the tip seal element 15b for the stationary spiral body 15.
As shown in Fig. 2, an oval shaped discharging port 16 is formed in the stationary plate 12, having the same cross-sectional area as that of the conventional discharging port of a circular shape and located at a position where it will not interfere with the tip seal element 15b during the orbital motion of the movable scroll member 3. The discharging port 16 has a longitudinal edge starting from a border of the arc S1 and the common tangent S3 and extending along the common tangent S3.
According to this type of compressor, the rotation of the drive shaft 4 is converted to an orbital motion of the movable scroll member 3 through the eccentric pin 10, by means of the driving bush 7 and the anti-spin mechanism 8. At a certain stage of this orbital motion, the movable scroll member 3 (movable spiral body 15) occupies a position as shown in Fig. 2 and then is 20~098Q
displaced therefrom to another position shown in Fig. 3, advanced by a phase angle of 90, around a center of the orbital motion not shown. At this position, a pair of compression chambers 5, 5 are united to form a single compression chamber. The tip-seal element 15b does not interfere with the discharging port 16 and suitably seals the single compression chamber 5. The compression chamber 5 is contracted more and more when the movable scroll member 3 occupies a position shown in Fig. 4 by a further displacement thereof by a phase angle of 90 from the position shown in Fig. 3. At this stage, the tip-seal element 15b approaches closer to the discharging port 16 but does not interfere with the discharging port 16 and maintains a suitable sealing of the gradually contracted compression chamber 5. Upon a further advance of the orbital motion by a phase angle of 90, the movable scroll member 3 occupies a position shown in Fig. 5, at which a volume of the single compression chamber 4 becomes almost zero. The longitudinal edge of the discharging port 16 along the common tangent S3 of the stationary spiral body 13 lies adjacent to the common tangent F3 of the movable spiral body 15, so that the discharging port 16 is substantially completely blocked by the beginning area 151 of the movable spiral body 15.
Although the tip-seal element 15b comes very close to the discharging port 16, it does not yet interfere with the discharging port 16. Upon further rotation of the movable scroll member 3, the tip-seal element 15b is moved farther from the discharging port 16, and thereafter the above steps are repeated.
Thus, as the volume of the compression chamber 5 decreases during the orbital motion of the movable scroll member 3, a coolant gas in the compression chamber 5 is pressurized to a pressure value identical to that of the conventional compressor, and the pressure thereof opens a valve (not shown) so that the gas is discharged from the discharging port 16 with the same cross-sectional area as that of the conventional circular one to a discharging chamber 6. The tip-seal element 13b in the stationary spiral body 13 operates in association with the movable side plate 14, in the same manner as the tip-seal element 15b, relative to the stationary side plate 12 as stated above.
In the scroll type compressor according to the present invention, since the tip-seal elements 13b and 15b are provided even at the beginning area of the stationary and movable spiral bodies 13 and 15 subjected to the maximum pressure in the course of the compression stroke, the sealability in this area is improved and pressure loss prevented.
As the discharging port 16 has an oval shape, to avoid an interference thereof with the tip-seal element 15b in the course of the orbital motion of the movable scroll member 3, the tendency for the tip-seal element 15b to be drawn from the groove 15a into the discharging port 16, and tnus to be damaged by the edge thereof, is eliminated. Further, the fluid pressure is maintained at the same level as in the case of the conventional circular discharging port, because the cross-sectional areas thereof are the same.
Accordingly, in this compressor, the leakage of the coolant gas is suppressed to a minimum value so that the drive force can be effectively utilized. Also, the life span of the tip-seal element can be prolonged due to the elimination of the damage by the discharging port.
In this connection, the discharging port 16 is not l mited to an oval but may be any shape, provided it is an elongated shape.
Another advantage of the present invention is as follows:
In this compressor, the tip-seal element is provided throughout the length of each of the stationary and movable spiral bodies, whereby the sealability between the stationary and movable scroll members can be suitably maintained even though a certain axial gap is formed therebetween, to avoid a direct contact of the two scroll members. This results in a reduction of the drive power and an improvement of the durability, due to a prolonging of the life span of the parts.
Grooves 22a and 32a are formed, respectively, along ridges of the stationary and movable spiral bodies 22 and 32, extending in the spiral direction thereof. As shown in Fig. 7, tip seal elements 22b and 32b are accommodated in the grooves 22a, 32a, respectively, for sealing a gap between the spiral bodies 22, 32 and the side plates 31, 21.
As shown in Fig. 6, the rotation of a drive shaft 54 is converted to an orbital motion of the movable scroll member 53 through an eccentric bush 57 and an anti-spin mechanism 58. The structures and functions of - 2 - 2~6 0~0 the eccentric bush and the anti-spin mechanism are described in detail in, for example, Japanese Unexamined Patent Publication (Xokai) No. 57-148087 or 57-148092.
According to the orbital motion of the movable scroll S member 53, a volume of a compression chamber 55 formed between the scroll members 52, 53 is gradually decreased while the compression chamber 55 is displaced to a central area of the scroll members, whereby a fluid in the compression chamber 55 is compressed and finally discharged therefrom through a discharging port 61 of the stationary side plate 21, into a discharging chamber 60.
At this stage, the tip seal element 32b is pressurized from the back by a coolant gas from a high pressure side HP positioned closer to the center of the stationary side plate 21, whereby the tip seal element 32 is brought into tight contact with a wall of the groove 32a adjacent to the low pressure side LP positioned farther from the center of the stationary side plate 21, and brought into tight contact with a surface of the stationary side plate 21 via a film of lubricant contained in the coolant gas, so that the coolant gas is sealed in the compression chamber 55. The tip seal element 22b functions in a similar manner.
In the conventional compressor, the tip seal element 32b is not provided in the beginning area of the movable spiral body 32. This is because, as shown in Fig. 8, the discharging port 61 of the conventional compressor has a circular shape, and if the tip seal element 32b were located in this area, the tip seal element 32b would be liable to be sucked from the groove 32a into the discharging port 61 when the tip seal element 32b overlapped the discharging port 61 in the course of the orbital motion of the movable scroll member 53, whereby the tip seal element 32b would be damaged by the edge of the latter. Accordingly, the conventional compressor has a drawback of an incomplete sealability at the beginning area of the movable spiral ~ 3 ~ 2~609~
body, and as this area is subjected to the maximum pressure during the compression process, a pressure loss is liable to occur.
SUMMARY OF THE INVENTION
The object of the present invention is to solve the above drawback of the prior art and to improve the sealability at the beginning area of the movable spiral body while preventing the damage of the tip seal element.
According to the present invention, a scroll type compressor is proposed, comprising a stationary scroll member consisting of a stationary side plate and a stationary spiral body integrally fixed therewith and a movable scroll member consisting of a movable side plate and a movable spiral body integrally fixed therewith;
both the scroll members being engaged with each other so that a plurality of compression chambers are formed between the scroll members and gradually decreased during an orbital motion of the movable scroll member around the stationary scroll member, while the movable scroll member is inhibited from spinning~on its own axis, whereby a fluid is compressed in the compression chambers and discharged from the compression chamber through a discharging port formed on the stationary side plate; the movable spiral body having a groove along a ridge thereof, extending in the spiral direction, in which groove a tip-seal element is accommodated for sealing a gap between the stationary side plate and the ridge of the movable spiral body; characterized in that the tip-seal element extends to the beginning area of the movable spiral body and in that the discharging port is formed in an elongated shape to thereby avoid an interference thereof with the tip-seal element during the orbital motion of the movable scroll member while a necessary cross-sectional area of the discharging port is maintained.
According to the present invention, the sealability is fully maintained even at the beginning area of the - 4 ~ 2~9~n movable spiral body subjected to the maximum pressure, because the tip-seal element is extended thereto, and thus a pressure loss in the compression chamber is avoided.
Moreover, as the discharging port is formed in an elongated shape, not in a circular shape, so that the interference thereof with the tip-seal element can be avoided and that the necessary cross-sectional area of the discharging port is maintained, a draw-in of the tip seal element from the groove to the discharging port is prevented and damage to the tip-seal element by the edge of the discharging port is avoided, while the necessary discharging efficiency is guaranteed.
BRIEF DESCRIPTION OF THE DRAWINGS
Other and further objects and advantages of the present invention will be apparent from the following description of the preferred embodiments with reference to the attached drawings: wherein Fig. 1 is a side sectional view of a scroll type compressor according to the present invention;
Fig. 2 is A-A section of Fig. l at a certain phase angle of the orbital motion of the movable scroll member;
Fig. 3 is A-A section of Fig. 1 at a phase angle advanced by 90 from that shown in Fig. 2;
Fig. 4 is A-A section of Fig. 1 at a phase angle advanced by 90 from that shown in Fig. 3;
Fig. 5 is A-A section of Fig. l at a phase angle advanced by 90 from that shown in Fig. 4;
Fig. 6 is a side sectional view of a conventional scroll type compressor;
Fig. 7 is an enlarged side sectional view of a main portion of the conventional compressor; and Fig. 8 is a cross-section of a main portion of the conventional compressor.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
As shown in Fig. l, in a scroll type compressor ~ 5 ~ 2~6098~
according to the present invention, a stationary scroll member 2 is fixed within a housing 1, and a movable scroll member 3 arranged in the housing l and a housing 9 is engaged with the stationary scroll member 2 so that a plurality of compression chambers 5 are formed between both the scroll members 2 and 3. A drive shaft 4 is supported in the housings 1, 9 via a bearing means, and an eccentric pin 10 is secured on an inner end surface of the driving shaft 4. At the bearing side end of the eccentric pin 10 is fixed a counterweight 11, and to the other end thereof is attached a driving bush 7 suppoxting the movable scroll member 3 by a bearing means, so that it can be subjected to an orbital motion around the stationary scroll member 2 in association with an anti-spin mechanism 8.
The movable scroll member 3 consists of a movableside plate 14 and an movable spiral body 15 integrally fixed therewith on one side of the side plate 14. As shown in Fig. 2, the movable spiral body 15 is formed by outer and inner walls, eac~h defined, except for the beginning area 151 thereof, by an involute curve obtained from a predetermined basic circle. Only the inner wall of the beginning area 151 is defined by an arc F1 having a radius r, an arc F2 having a radius R (r + radius of orbital motion) and a common tangent F3 for the two arcs.
Along a ridge of the movable spiral body 15 is extended a groove 15a, from the beginning area 151 to the ending area thereof (not shown), while an equal wall thickness is maintained between the groove and the outer wall of the spiral body 15. A tip-seal element 15b made of PTFE
(polytetrafluoroethylene) is accommodated within the groove 15a, for sealing a gap between the stationary side plate 12 and the tip end of the spiral body 15. A more detailed explanation will be made later of the tip-seal element.
As shown in Fig. 1, the stationary scroll member 2 20~0980 consists of a stationary side plate 12 and a stationary spiral body 13 integrally fixed therewith on one side of the side plate 12. As shown in Fig. 2, the stationary spir~l body 13 is formed by outer and inner walls, each defined, except for the beginning area 131 thereof, by an involute curve obtained from a predetermined basic circle. Only the inner wall of the beginning area 131 is defined by an arc Sl having a radius r, an arc S2 having a radius R (r + radius of orbital motion) and a common tangent S3 for the two arcs. Along a ridge of the stationary spiral body 13 is also extended a groove 13a.
A tip-seal element 13b made of PTFE
(polytetrafluoroethylene) is accommodated within the groove 13a, for sealing a gap between the movable side plate 14 and the tip end of the spiral body 13. This tip seal element 13b is provided in the beginning area 131 (although not shown in the drawing), as in the case of the tip seal element 15b for the stationary spiral body 15.
As shown in Fig. 2, an oval shaped discharging port 16 is formed in the stationary plate 12, having the same cross-sectional area as that of the conventional discharging port of a circular shape and located at a position where it will not interfere with the tip seal element 15b during the orbital motion of the movable scroll member 3. The discharging port 16 has a longitudinal edge starting from a border of the arc S1 and the common tangent S3 and extending along the common tangent S3.
According to this type of compressor, the rotation of the drive shaft 4 is converted to an orbital motion of the movable scroll member 3 through the eccentric pin 10, by means of the driving bush 7 and the anti-spin mechanism 8. At a certain stage of this orbital motion, the movable scroll member 3 (movable spiral body 15) occupies a position as shown in Fig. 2 and then is 20~098Q
displaced therefrom to another position shown in Fig. 3, advanced by a phase angle of 90, around a center of the orbital motion not shown. At this position, a pair of compression chambers 5, 5 are united to form a single compression chamber. The tip-seal element 15b does not interfere with the discharging port 16 and suitably seals the single compression chamber 5. The compression chamber 5 is contracted more and more when the movable scroll member 3 occupies a position shown in Fig. 4 by a further displacement thereof by a phase angle of 90 from the position shown in Fig. 3. At this stage, the tip-seal element 15b approaches closer to the discharging port 16 but does not interfere with the discharging port 16 and maintains a suitable sealing of the gradually contracted compression chamber 5. Upon a further advance of the orbital motion by a phase angle of 90, the movable scroll member 3 occupies a position shown in Fig. 5, at which a volume of the single compression chamber 4 becomes almost zero. The longitudinal edge of the discharging port 16 along the common tangent S3 of the stationary spiral body 13 lies adjacent to the common tangent F3 of the movable spiral body 15, so that the discharging port 16 is substantially completely blocked by the beginning area 151 of the movable spiral body 15.
Although the tip-seal element 15b comes very close to the discharging port 16, it does not yet interfere with the discharging port 16. Upon further rotation of the movable scroll member 3, the tip-seal element 15b is moved farther from the discharging port 16, and thereafter the above steps are repeated.
Thus, as the volume of the compression chamber 5 decreases during the orbital motion of the movable scroll member 3, a coolant gas in the compression chamber 5 is pressurized to a pressure value identical to that of the conventional compressor, and the pressure thereof opens a valve (not shown) so that the gas is discharged from the discharging port 16 with the same cross-sectional area as that of the conventional circular one to a discharging chamber 6. The tip-seal element 13b in the stationary spiral body 13 operates in association with the movable side plate 14, in the same manner as the tip-seal element 15b, relative to the stationary side plate 12 as stated above.
In the scroll type compressor according to the present invention, since the tip-seal elements 13b and 15b are provided even at the beginning area of the stationary and movable spiral bodies 13 and 15 subjected to the maximum pressure in the course of the compression stroke, the sealability in this area is improved and pressure loss prevented.
As the discharging port 16 has an oval shape, to avoid an interference thereof with the tip-seal element 15b in the course of the orbital motion of the movable scroll member 3, the tendency for the tip-seal element 15b to be drawn from the groove 15a into the discharging port 16, and tnus to be damaged by the edge thereof, is eliminated. Further, the fluid pressure is maintained at the same level as in the case of the conventional circular discharging port, because the cross-sectional areas thereof are the same.
Accordingly, in this compressor, the leakage of the coolant gas is suppressed to a minimum value so that the drive force can be effectively utilized. Also, the life span of the tip-seal element can be prolonged due to the elimination of the damage by the discharging port.
In this connection, the discharging port 16 is not l mited to an oval but may be any shape, provided it is an elongated shape.
Another advantage of the present invention is as follows:
In this compressor, the tip-seal element is provided throughout the length of each of the stationary and movable spiral bodies, whereby the sealability between the stationary and movable scroll members can be suitably maintained even though a certain axial gap is formed therebetween, to avoid a direct contact of the two scroll members. This results in a reduction of the drive power and an improvement of the durability, due to a prolonging of the life span of the parts.
Claims (4)
1. A scroll type compressor comprising:
a stationary scroll member consisting of a stationary side plate and a stationary spiral body integrally fixed therewith; and a movable scroll member consisting of a movable side plate and a movable spiral body integrally fixed therewith;
both scroll members being engaged with each other so that a plurality of compression chambers are formed between the scroll members and gradually decreased during an orbital motion of the movable scroll member around the stationary scroll member, while the movable scroll member is inhibited from spinning on its own axis;
whereby a fluid is compressed in the compression chambers and discharged from the compression chamber through a discharging port formed on the stationary side plate; the movable spiral body having a groove along a ridge thereof, extending in the spiral direction, in which groove a tip-seal element is accommodated for sealing a gap between the stationary side plate and the ridge of the movable spiral body;
characterized in that the tip-seal element extends to the beginning area of the movable spiral body; and in that the discharging port is formed in an elongated shape to avoid an interference thereof with the tip-seal element during the orbital motion of the movable scroll member while a necessary cross-sectional area of the discharging port is maintained.
a stationary scroll member consisting of a stationary side plate and a stationary spiral body integrally fixed therewith; and a movable scroll member consisting of a movable side plate and a movable spiral body integrally fixed therewith;
both scroll members being engaged with each other so that a plurality of compression chambers are formed between the scroll members and gradually decreased during an orbital motion of the movable scroll member around the stationary scroll member, while the movable scroll member is inhibited from spinning on its own axis;
whereby a fluid is compressed in the compression chambers and discharged from the compression chamber through a discharging port formed on the stationary side plate; the movable spiral body having a groove along a ridge thereof, extending in the spiral direction, in which groove a tip-seal element is accommodated for sealing a gap between the stationary side plate and the ridge of the movable spiral body;
characterized in that the tip-seal element extends to the beginning area of the movable spiral body; and in that the discharging port is formed in an elongated shape to avoid an interference thereof with the tip-seal element during the orbital motion of the movable scroll member while a necessary cross-sectional area of the discharging port is maintained.
2. A scroll type compressor as defined by claim 1, wherein the respective spiral body is formed by outer and inner walls, each defined by an involute curve except for the beginning area of the inner wall, which area is defined by a small arc having a radius r and a large arc having a radius (r + radius of orbital motion) and a tangent common to these arcs.
3. A scroll type compressor as defined by claim 2, wherein the discharging port is positioned in the stationary side plate so that the elongated edge thereof is adjacent in parallel to the common tangent area in the inner wall of the stationary spiral body.
4. A scroll type compressor as defined as defined by claim 1, wherein the tip-seal element is made of polytetrafluoroethylene resin.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991006934U JPH04104191U (en) | 1991-02-19 | 1991-02-19 | scroll compressor |
| JP3-6934 | 1991-02-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2060980A1 true CA2060980A1 (en) | 1992-08-20 |
Family
ID=11652087
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2060980 Abandoned CA2060980A1 (en) | 1991-02-19 | 1992-02-11 | Scroll type compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US5217358A (en) |
| JP (1) | JPH04104191U (en) |
| CA (1) | CA2060980A1 (en) |
| DE (1) | DE4204872A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5242283A (en) * | 1991-03-15 | 1993-09-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor with elongated discharge port |
| JPH05321855A (en) * | 1992-05-21 | 1993-12-07 | Toyota Autom Loom Works Ltd | Seal structure for scroll type compressor |
| JP3036271B2 (en) * | 1992-12-03 | 2000-04-24 | 株式会社豊田自動織機製作所 | Scroll compressor |
| US20060269433A1 (en) * | 2005-05-31 | 2006-11-30 | Skinner Robin G | Discharge port for a scroll compressor |
| JP2007046492A (en) * | 2005-08-08 | 2007-02-22 | Sanden Corp | Scroll compressor |
| US8297958B2 (en) * | 2009-09-11 | 2012-10-30 | Bitzer Scroll, Inc. | Optimized discharge port for scroll compressor with tip seals |
| JPWO2023120619A1 (en) * | 2021-12-23 | 2023-06-29 |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6041237B2 (en) * | 1981-03-09 | 1985-09-14 | サンデン株式会社 | Scroll type fluid device |
| JPS57212302A (en) * | 1981-06-24 | 1982-12-27 | Hitachi Ltd | Displacement type scroll hydraulic machine |
| JPS5958187A (en) * | 1982-09-26 | 1984-04-03 | Sanden Corp | Scroll type compressor |
| GB2167133B (en) * | 1984-11-19 | 1988-04-07 | Sanden Corp | Scroll-type rotary fluid-machine |
| JPS6287638A (en) * | 1985-10-15 | 1987-04-22 | Toyota Motor Corp | Fuel pressure control device for internal combustion engine |
| JPH0756272B2 (en) * | 1985-11-15 | 1995-06-14 | ダイキン工業株式会社 | Scroll type fluid machine |
| JPS63215891A (en) * | 1987-03-02 | 1988-09-08 | Sanyo Electric Co Ltd | Scroll compressor |
| US4886434A (en) * | 1987-02-20 | 1989-12-12 | Sanyo Electric Co., Ltd. | Scroll compressor having discharge part communicating with two compression spaces simultaneously |
| JP2713937B2 (en) * | 1988-01-19 | 1998-02-16 | 三洋電機株式会社 | Scroll compressor |
| US5022834A (en) * | 1990-01-16 | 1991-06-11 | Carrier Corporation | Scroll compressor with enhanced discharge port |
-
1991
- 1991-02-19 JP JP1991006934U patent/JPH04104191U/en active Pending
-
1992
- 1992-01-31 US US07/829,978 patent/US5217358A/en not_active Expired - Fee Related
- 1992-02-11 CA CA 2060980 patent/CA2060980A1/en not_active Abandoned
- 1992-02-18 DE DE19924204872 patent/DE4204872A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| DE4204872A1 (en) | 1992-08-20 |
| US5217358A (en) | 1993-06-08 |
| JPH04104191U (en) | 1992-09-08 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |